Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
Inventive embodiments are directed to components, subassemblies, systems, and/or methods for infinitely variable transmissions (IVT). In one embodiment, a control system is adapted to facilitate a change in the ratio of an IVT. In another embodiment, a control system includes a carrier member configured to have a number of radially offset slots. Various inventive carrier members and carrier drivers can be used to facilitate shifting the ratio of an IVT. In some embodiments, the traction planet assemblies include planet axles configured to cooperate with the carrier members. In one embodiment, the carrier member is configured to rotate and apply a skew condition to each of the planet axles. In some embodiments, a carrier member is operably coupled to a carrier driver. In some embodiments, the carrier member is configured to couple to a source of rotational power. Among other things, shift control interfaces for an IVT are disclosed.
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This application is a continuation of U.S. application Ser. No. 13/035,683, filed Feb. 25, 2011, which claims the benefit of U.S. Provisional Patent Application No. 61/310,224, filed Mar. 3, 2010. The disclosures of all of the above-referenced prior applications, publications, and patents are considered part of the disclosure of this application, and are incorporated by reference herein in their entirety.
BACKGROUND OF THE INVENTION1. Field of the Invention
The field of the invention relates generally to transmissions, and more particularly the inventive embodiments related to continuously variable transmissions (CVTs) and infinitely variable transmissions (IVTs).
2. Description of the Related Art
In certain systems, power is characterized by torque and rotational speed. More specifically, power in these systems is generally defined as the product of torque and rotational speed. Typically, a transmission couples to a power input that provides an input torque at an input speed. The transmission also couples to a load that demands an output torque and output speed, which may differ from the input torque and the input speed. Typically, and generalizing, a prime mover provides the power input to the transmission, and a driven device or load receives the power output from the transmission. A primary function of the transmission is to modulate the power input in such a way to deliver a power output to the driven device at a desired ratio of input speed to output speed (“speed ratio”).
Some mechanical drives include transmissions of the type known as stepped, discrete, or fixed ratio. These transmissions are configured to provide speed ratios that are discrete or stepped in a given speed ratio range. For example, such a transmission may provide for a speed ratio of 1:2, 1:1, or 2:1, but such a transmission cannot deliver intermediate speed ratios such as 1:1.5, 1:1.75, 1.5:1, or 1.75:1, for example. Other drives include a type of transmission generally known as a continuously variable transmission (or “CVT”), which includes a continuously variable variator. A CVT, in contrast to a stepped transmission, is configured to provide every fractional ratio in a given speed ratio range. For example, in the speed ratio range mentioned above, a CVT is generally capable of delivering any desired speed ratio between 1:2 and 2:1, which would include speed ratios such as 1:1.9, 1:1.1, 1.3:1, 1.7:1, etc. Yet other drives employ an infinitely variable transmission (or “IVT”). An IVT, like a CVT, is capable of producing every speed ratio in a given ratio range. However, in contrast to a CVT, the IVT is configured to deliver a zero output speed (a “powered zero” state) with a steady input speed. Hence, given the definition of speed ratio as the ratio of input speed to output speed, the IVT is capable of delivering an infinite set of speed ratios, and consequently, the IVT is not limited to a given ratio range. It should be noted that some transmissions use a continuously variable variator coupled to other gearing and/or clutches in a split powered arrangement to produce IVT functionality. However, as used here, the term IVT is primarily understood as comprehending an infinitely variable variator which produces IVT functionality without being necessarily coupled to additional gearing and/or clutches.
The field of mechanical power transmission is cognizant of continuous or infinitely variable variators of several types. For example, one well known class of continuous variators is the belt-and-variable-radius-pulley variator. Other known variators include hydrostatic, toroidal, and cone-and-ring variators. In some cases, these variators couple to other gearing to provide IVT functionality. Some hydromechanical variators can provide infinite ratio variability without additional gearing. Some variators, continuously and/or infinitely variable, are classified as frictional or traction variators because they rely on dry friction or elastohydrodynamic traction, respectively, to transfer torque across the variator. One example of a traction variator is a ball variator in which spherical elements are clamped between torque transfer elements and a thin layer of elastohydrodynamic fluid serves as the torque transfer conduit between the spherical and the torque transfer elements. It is to this latter class of variators that the inventive embodiments disclosed here are most related.
There is a continuing need in the CVT/IVT industry for transmission and variator improvements in increasing efficiency and packaging flexibility, simplifying operation, and reducing cost, size, and complexity, among other things. The inventive embodiments of the CVT and/or IVT methods, systems, subassemblies, components, etc., disclosed below address some or all of the aspects of this need.
SUMMARY OF THE INVENTIONThe systems and methods herein described have several features, no single one of which is solely responsible for its desirable attributes. Without limiting the scope as expressed by the claims that follow, its more prominent features will now be discussed briefly. After considering this discussion, and particularly after reading the section entitled “Detailed Description of Certain Inventive Embodiments” one will understand how the features of the system and methods provide several advantages over traditional systems and methods.
One aspect of the invention relates to a shifting mechanism for an infinitely variable transmission (IVT) having a longitudinal axis and a set of traction planet assemblies arranged angularly about the longitudinal axis. In one embodiment, the shifting mechanism has a first carrier member coupled to each of the traction planet assemblies. The first carrier member is configured to guide the traction planet assemblies. The shifting mechanism has a second carrier member coupled to each of the traction planet assemblies. The second carrier member is configured to guide the traction planet assemblies. The first carrier member is capable of rotating with respect to the second carrier member. A carrier driver nut is coupled to the first carrier member. The carrier driver nut is adapted to translate axially. An axial translation of the carrier driver nut corresponds to a rotation of the first carrier member with respect to the second carrier member.
One aspect of the invention relates to an infinitely variable transmission (IVT) having a longitudinal axis. In one embodiment, the IVT has a number of traction planet assemblies arranged angularly about the longitudinal axis. The IVT is provided with a first carrier member coupled to each of the traction planet assemblies. The first carrier member is provided with a number of radially off-set slots. The first carrier member is configured to guide the traction planet assemblies. The IVT can include a second carrier member coupled to each of the traction planet assemblies. The second carrier member is provided with a number of radial slots. The first and second carrier members are configured to receive a rotational power input. In one embodiment, the first carrier member is capable of rotating with respect to the second carrier member. The IVT also includes a carrier driver nut coupled to the first carrier member. The carrier driver nut is adapted to translate axially. An axial translation of the carrier driver nut corresponds to a rotation of the first carrier member with respect to the second carrier member. In an alternative embodiment, the IVT has a main shaft positioned along the longitudinal axis. The main shaft is operably coupled to the first and second carrier members. The main shaft can have a set of helical splines that are configured to couple to a carrier driver nut. In yet another alternative embodiment, the carrier driver nut is adapted to translate axially along the main shaft. An axial translation of the carrier driver nut corresponds to a rotation of the carrier driver nut. In some embodiments, the IVT has a first traction ring coupled to each traction planet assembly. The first traction ring is substantially non-rotatable about the longitudinal axis. The IVT can be provided with a second traction ring coupled to each traction planet assembly. The second traction ring is adapted to provide a power output from the IVT. In an alternative embodiment, the first and second carrier members are adapted to receive the rotational power from the main shaft. In one embodiment, the IVT has a shift fork operably coupled to the carrier driver nut. The shift fork can have a pivot axis that is off-set from the longitudinal axis. A pivoting of the shift fork corresponds to an axial translation of the carrier driver nut. The axial translation of the carrier driver nut corresponds to a rotation of the carrier driver about the longitudinal axis. In an alternative embodiment, the IVT is provided with a pump operably coupled to the main shaft. In yet another embodiment, the IVT has a ground ring coupled to the first traction ring. The ground ring is coupled to a housing of the IVT.
Another aspect of the invention concerns an infinitely variable transmission (IVT) having a longitudinal axis. The IVT includes a main shaft arranged along the longitudinal axis. The main shaft is provided with a set of helical splines. The IVT has a group of traction planet assemblies arranged angularly about the longitudinal axis. In one embodiment, the IVT has a first carrier member coupled to each of the traction planet assemblies. The first carrier member is provided with a number of radially off-set slots. The first carrier member is configured to guide the traction planet assemblies. The IVT includes a second carrier member coupled to each of the traction planet assemblies. The second carrier member is provided with a number of radial slots. The first and second carrier members are coupled to a rotational power source. In one embodiment, the IVT includes a shifting mechanism having a shift fork. The shift fork has a pivot pin off-set from the longitudinal axis. The shifting mechanism includes a carrier driver nut operably coupled to the shift fork. The carrier driver nut has an inner bore configured to engage the helical splines of the main shaft. The carrier driver nut is configured to rotate about the longitudinal axis. In one embodiment, a movement of the shift fork about the pivot pin corresponds to an axial movement of the carrier driver nut. An axial movement of the carrier driver nut corresponds to a rotation of the first carrier member with respect to the second carrier member. In some embodiments, the IVT has a first traction ring in contact with each traction planet assembly. The first traction ring is substantially non-rotatable about the main shaft. The IVT can have a second traction ring in contact with each traction planet assembly. The second traction ring is adapted to provide a power output from the IVT. In some embodiments, an output shaft is operably coupled to the second traction ring. In an alternative embodiment, a disengagement mechanism is operably coupled to the output shaft. In yet another embodiment, a torque limiter is coupled to the second carrier member. The torque limiter can also be coupled to the main shaft. In some embodiments, the torque limiter includes a number of springs coupled to the second carrier member and the main shaft.
One aspect of the invention concerns a shifting mechanism for an infinitely variable transmission (IVT) having a main shaft arranged along a longitudinal axis of the IVT and a group of traction planet assemblies arranged angularly about the main shaft. The traction planet assemblies are coupled to first and second carrier members. The first carrier member is provided with a number of radially off-set guide slots. The first and second carrier members are adapted to receive a rotational power. In one embodiment, the shifting mechanism includes a shift fork. The shift fork has a pivot pin off-set from the longitudinal axis. The shifting mechanism has a carrier driver nut operably coupled to the shift fork. The carrier driver nut has an inner bore configured to engage a number of helical splines formed on the main shaft. The carrier driver nut is configured to rotate about the longitudinal axis. The carrier driver nut is adapted to axially translate along the longitudinal axis. A movement of the shift fork about the pivot pin corresponds to an axial movement of the carrier driver nut. An axial movement of the carrier driver nut corresponds to a rotation of the first carrier member with respect to the second carrier member. In an alternate embodiment, the shifting mechanism includes a shift collar operably coupled to the shift fork. A bearing can be coupled to the shift collar and be adapted to couple to the carrier driver nut. In yet another embodiment, the shifting mechanism has a rocker arm coupled to the shift fork.
Another aspect of the invention concerns an infinitely variable transmission (IVT) having a longitudinal axis. The IVT has a group of traction planets arranged angularly about the longitudinal axis. The IVT includes a first carrier member coupled to each of the traction planet assemblies. The first carrier member is provided with a number of radially off-set slots. The first carrier member is configured to guide the traction planet assemblies. The IVT has a second carrier member coupled to each of the traction planet assemblies. The second carrier member is provided with a group of radial slots. The first and second carrier members are coupled to a rotational power source. In one embodiment, the IVT has a carrier driver positioned radially outward of the first and second carrier members. The carrier driver has a number of longitudinal grooves. At least one groove is aligned parallel with the longitudinal axis, and said groove is coupled to the first carrier member. In one embodiment, at least one groove is angled with respect to the longitudinal axis, and said groove is coupled to the second carrier member. In other embodiments, the carrier driver is adapted to translate axially. In some embodiments, the axial translation of the carrier driver corresponds to a rotation of the first carrier member with respect to the second carrier member. In still other embodiments, the IVT has a pump coupled to the first carrier member.
Another aspect of the invention relates to an infinitely variable transmission (IVT) having a longitudinal axis. In one embodiment, the IVT has a number of traction planets arranged angularly about the longitudinal axis. The IVT is provided with a first carrier member coupled to each of the traction planet assemblies. The first carrier member is provided with a number of radially off-set slots. The radially off-set slots are configured to guide the traction planet assemblies. The first carrier member is provided with a number of longitudinal guide slots, and said longitudinal guide slots are formed at an angle with respect to the longitudinal axis. In one embodiment, the IVT has a second carrier member coupled to each of the traction planet assemblies. The second carrier member is provided with a number of radial slots. The radial slots are configured to guide the traction planet assemblies. The second carrier member is provided with a number of longitudinal guide slots, and said longitudinal guide slots are arranged parallel to the longitudinal axis. In one embodiment, the first and second carrier members are configured to couple to a rotational power source. The IVT also has a carrier driver coupled to the first and second carrier members. The carrier driver is adapted to rotate about the longitudinal axis. The carrier driver is adapted to translate axially. In one embodiment, an axial translation of the carrier driver corresponds to a rotation of the first carrier member with respect to the second carrier member. In some embodiments, the carrier driver has a set of shift pins extending radially outward from a central cylindrical hub. The cylindrical hub is coaxial with the longitudinal axis. In other embodiments, the IVT has a spring coupled to the carrier driver. In yet other embodiments, an axial translation of the carrier driver corresponds to a change in the transmission ratio of the IVT.
Another aspect of the invention concerns a shifting mechanism for an infinitely variable transmission (IVT) having a group of traction planet assemblies. In one embodiment, the shifting mechanism has a first carrier member having a number of radially off-set guide slots. The radially off-set guide slots are arranged to guide the traction planet assemblies. The first carrier member has a number of longitudinal slots, and said longitudinal slots angled with respect to the longitudinal axis. The shifting mechanism includes a second carrier member has a number of guide slots arranged about the longitudinal axis. The guide slots are arranged to guide the traction planet assemblies. The second carrier member has a number of longitudinal slots, and said longitudinal slots parallel to the longitudinal axis. The shifting mechanism has a carrier driver coupled to the first and second carrier members. The carrier driver has a number of shift pins extending from a central hub. The shift pins engage the longitudinal slots formed on the first and second carrier members. An axial translation of the carrier driver corresponds to a rotation of the first carrier member with respect to the second carrier member. In some embodiments, the carrier driver, the first carrier member, and the second carrier member are configured to rotate about the longitudinal axis at a speed substantially equal to an input speed of a power source coupled to the IVT. In other embodiments, the shifting mechanism has a shift roller coupled to each shift pin. The shift roller is in contact with the longitudinal slots of the first carrier member.
Another aspect of the invention relates to a method of controlling an infinitely variable transmission (IVT) having a longitudinal axis. The method includes the step of providing a group of traction planet assemblies arranged angularly about the longitudinal axis. The method can include providing a first carrier member coupled to each traction planet assembly. The first carrier member has a number of radially off-set guide slots arranged to guide the traction planet assemblies. In one embodiment, the method includes the step of providing a second carrier member coupled to each traction planet assembly. The second carrier member has a number of radial guide slots arranged to guide the traction planet assemblies. The method can include the step of coupling the first and second carrier members to a rotational power source. The method includes providing a carrier driver nut coupled to the first carrier member. The method also includes the step of translating the carrier driver nut along the longitudinal axis. In an alternative embodiment, the step of translating the carrier driver nut includes the step of rotating the first carrier member with respect to the second carrier member. In some embodiments, the method includes the step of operably coupled the carrier driver nut to a shift fork. In some embodiments, the method includes the step of coupling a toque limiter to the second carrier member. In yet other embodiments, the method includes coupling the torque limiter to the rotational source of power. In some embodiments, the method includes the step of sensing a torque applied to the second carrier member. The method can also include the step of rotating the second carrier member based at least in part on the sensed torque. Rotating the second carrier member can include the step of adjusting the transmission ratio.
The preferred embodiments will be described now with reference to the accompanying figures, wherein like numerals refer to like elements throughout. The terminology used in the descriptions below is not to be interpreted in any limited or restrictive manner simply because it is used in conjunction with detailed descriptions of certain specific embodiments of the invention. Furthermore, embodiments of the invention can include several inventive features, no single one of which is solely responsible for its desirable attributes or which is essential to practicing the inventions described. Certain continuously variable transmission (CVT) and infinitely variable transmission (IVT) embodiments described here are generally related to the type disclosed in U.S. Pat. Nos. 6,241,636; 6,419,608; 6,689,012; 7,011,600; 7,166,052; U.S. patent application Ser. Nos. 11/243,484 and 11/543,311; and Patent Cooperation Treaty patent applications PCT/IB2006/054911, PCT/US2008/068929, PCT/US2007/023315, PCT/US2008/074496, and PCT/US2008/079879. The entire disclosure of each of these patents and patent applications is hereby incorporated herein by reference.
As used here, the terms “operationally connected,” “operationally coupled”, “operationally linked”, “operably connected”, “operably coupled”, “operably linked,” and like terms, refer to a relationship (mechanical, linkage, coupling, etc.) between elements whereby operation of one element results in a corresponding, following, or simultaneous operation or actuation of a second element. It is noted that in using said terms to describe inventive embodiments, specific structures or mechanisms that link or couple the elements are typically described. However, unless otherwise specifically stated, when one of said terms is used, the term indicates that the actual linkage or coupling may take a variety of forms, which in certain instances will be readily apparent to a person of ordinary skill in the relevant technology.
For description purposes, the term “radial” is used here to indicate a direction or position that is perpendicular relative to a longitudinal axis of a transmission or variator. The term “axial” as used here refers to a direction or position along an axis that is parallel to a main or longitudinal axis of a transmission or variator. For clarity and conciseness, at times similar components labeled similarly.
It should be noted that reference herein to “traction” does not exclude applications where the dominant or exclusive mode of power transfer is through “friction.” Without attempting to establish a categorical difference between traction and friction drives here, generally these may be understood as different regimes of power transfer. Traction drives usually involve the transfer of power between two elements by shear forces in a thin fluid layer trapped between the elements. The fluids used in these applications usually exhibit traction coefficients greater than conventional mineral oils. The traction coefficient (μ) represents the maximum available traction forces which would be available at the interfaces of the contacting components and is a measure of the maximum available drive torque. Typically, friction drives generally relate to transferring power between two elements by frictional forces between the elements. For the purposes of this disclosure, it should be understood that the IVTs described here may operate in both tractive and frictional applications. For example, in the embodiment where an IVT is used for a bicycle application, the IVT can operate at times as a friction drive and at other times as a traction drive, depending on the torque and speed conditions present during operation.
Embodiments of the invention disclosed here are related to the control of a variator and/or an IVT using generally spherical planets each having a tiltable axis of rotation (sometimes referred to here as a “planet axis of rotation”) that can be adjusted to achieve a desired ratio of input speed to output speed during operation. In some embodiments, adjustment of said axis of rotation involves angular misalignment of the planet axis in a first plane in order to achieve an angular adjustment of the planet axis of rotation in a second plane, thereby adjusting the speed ratio of the variator. The angular misalignment in the first plane is referred to here as “skew” or “skew angle”. This type of variator control is generally described in U.S. patent application Ser. Nos. 12/198,402 and 12/251,325, the entire disclosure of each of these patent applications is hereby incorporated herein by reference. In one embodiment, a control system coordinates the use of a skew angle to generate forces between certain contacting components in the variator that will tilt the planet axis of rotation in the second plane. The tilting of the planet axis of rotation adjusts the speed ratio of the variator. Embodiments of skew control systems (sometimes referred to here as “skew based control systems”) and skew angle actuation devices for attaining a desired speed ratio of a variator will be discussed.
Embodiments of an infinitely variable transmission (IVT), and components and subassemblies thereof, will be described now with reference to
Referring now to
Referring now to
Referring now to
Turning now to
During operation of the IVT 100, a change in transmission ratio is achieved by rotating the actuator coupling 108. In some embodiments, the actuator coupling 108 is attached to a user control (not shown) that can be a mechanical linkage actuated with a user's hand. In other embodiments, the actuator coupling 108 can be coupled to an electrical or hydraulic actuator that can impart a rotary motion to the actuator coupling 108 that is indicative of the desired transmission ratio for IVT 100. Since the actuator coupling 108 is axially fixed with respect to the longitudinal axis, a rotation of the actuator coupling 108 tends to rotate the rocker arm 142 to thereby rotate and axially translate the pivot 143. Movement of the pivot 143 tends to rotate the shift fork 144 about the pivot pin 146. The pivot pin 146 is off-set from the main shaft 110 so that a rotation of the shift fork 144 about the pivot pin 146 corresponds to an axial translation of the slots 154. The axial movement of the slots 154 tends to axially move the shift collar 148 with respect to the main shaft 110. Since the carrier driver nut 152 is operably coupled to the shift collar 148, an axial translation of the shift collar 148 corresponds to an axial translation of the carrier driver nut 152. The carrier driver nut 152 couples to the helical splines 160 of the main shaft 110. An axial translation of the carrier driver nut 152 facilitates a relative rotation of the carrier driver nut 152 with respect to the main shaft 110. Since the carrier driver nut 152 engages the guide surfaces 164 of the first carrier member 116, a rotation of the carrier driver nut 152 with respect to the main shaft 110 corresponds to a rotation of the first carrier member 116 with respect to the main shaft 110. A rotation of the first carrier member 116 with respect to the second carrier member 118 tends to change the transmission ratio of the IVT 100.
It should be noted that a designer can configure the position of the rocker 142, the pivot 143, and the pivot pin 146 relative to the slots 154 to achieve a desired relationship between a rotation applied to the actuator coupling 108 and the axial displacement of the carrier driver nut 152. In some embodiments, a designer may select the position of the rocker 142, the pivot 143, and the pivot pin 146 to provide a desired force or torque applied to the actuator coupling 108 to achieve a change in transmission ratio. Likewise, a designer can select the pitch and lead of the helical splines 160 to achieve a desired relationship between an axial displacement of the carrier driver nut 152 and a rotation of the first carrier member 116.
Referring again to
Passing now to
Referring specifically to
During operation of the IVT 200, a change in transmission ratio can be achieved by axially translating the shift clevis 214. An axial translation of the shift clevis 214 tends to axially translate the carrier driver ring 212. An axial translation of the carrier driver ring 212 tends to guide the dowels 228, 230 in the grooves 220, 222, respectively. Since the first and second carrier members 208, 210 are substantially fixed in the axial direction, the first and second carrier members 208, 210 rotate relative to each other as the dowels 228, 230 travel axially in the grooves 220, 222, respectively.
Referring specifically now to
Passing now to
Turning now to
During operation of the IVT 400, a change in transmission ratio is achieved by axially translating actuator coupling 422. An axial translation of the actuator coupling 422 tends to axially translate the carrier driver nut 418. Since the carrier driver nut 418 engages the main shaft 404 on helical splines 420, an axial translation of the carrier driver nut 418 with respect to the main shaft 404 tends to facilitate a relative rotation between the carrier driver nut 418 and the main shaft 404. The torsion plate 416 rotates as the carrier driver nut 418 rotates, which tends to rotate the second carrier member 414 with respect to the first carrier member 412.
Referring now to
In one embodiment, the IVT 500 is provided with a center shaft 526 that substantially defines a longitudinal axis of the IVT 500. The center shaft 526 can be configured to support the first and second carrier members 514, 516. In some embodiments, the second carrier member 516 is rigidly attached to the center shaft 526. The first carrier member 514 can be piloted onto the center shaft 526 so that the first carrier member 514 can rotate with respect to the second carrier member 516. One end of the center shaft 526 can be configured to support an actuator coupling 528. In one embodiment, a bearing 529 supports the actuator coupling 528 on the center shaft 514. The bearing 529 is configured to allow axial translation of the actuator coupling 528 with respect to the center shaft 526. The actuator coupling 528 is attached to the housing 524 with splines and is substantially non-rotatable with respect to the center shaft 526. In one embodiment, the actuator coupling 528 is coupled to a linear actuator (not shown) to facilitate an axial translation of the actuator coupling 528. The actuator coupling 528 couples with a bearing 530 to a carrier driver hub 532. The carrier driver hub 532 couples to the first and second carrier members 514, 516.
Referring now specifically to
During operation of the IVT 500, a change in transmission ratio is achieved by axially translating the actuator coupling 528. The axial translation of the actuator coupling 528 tends to axially translate the carrier driver hub 532. As the carrier driver hub 532 translates axially, the rods 534 and rollers 536 axially translate along the longitudinal slots 538, 540, respectively. Since the longitudinal slots 540 are angled with respect to the longitudinal slots 540, an axial translation of the rods 534 and rollers 536 causes a relative rotation between the first carrier member 514 and the second carrier member 516, and thereby tends to change the ratio of the IVT 500. In some embodiments, the IVT 500 can be provided with a spring 542 configured to urge the carrier driver hub 532 to one axial end of the IVT 500.
Referring now to
Still referring to
In some embodiments, the IVT 600 can be provided with a torque limiter 630 that couples to the second carrier member 618 and the main shaft 610. The IVT 600 can also be provided with a pump assembly 635 coupled to the main shaft 610 (see for example,
Referring now to
During operation of the IVT 600, a shift in the transmission ratio can be achieved by moving the actuator linkage 642 to thereby rotate the shift actuator 608. A rotation of the shift actuator 608 corresponds to pivoting of the shift fork 644 about the axis 646. The pivoting of the shift fork 644 urges the shift collar 648 axially with respect to the main shaft 610. The shift collar 648 thereby axially translates the bearing 650 and carrier driver nut 652. The helical splines 654 tend to rotate the carrier driver nut 652 as the carrier driver nut 652 moves axially. The rotation of the carrier driver nut 652 is typically a small angle. The carrier extension 656, and consequently the first carrier member 616, is guided through a rotation by the carrier driver nut 652. As explained previously in reference to
In one embodiment, the helical splines 654 have a lead in the range of 200-1000 mm. For some applications, the lead is in the range of 400-800 mm. The lead is related to how much friction is in the system that can counteract a phenomenon known as back torque shifting. The lead can be sized to reduce the input force on the carrier driver nut 652, the required rotation of the first carrier member 616 to shift through the ratio, and available package space. The sizing of the lead is subject to design requirements, and could also be impacted by testing results.
Turning now to
In one embodiment, the torque limiter 630 includes a carrier cap 676 coupled to the second carrier member 618. In some embodiments, the spring carrier 668 is axially located between the second carrier member 618 and the carrier cap 676. The carrier cap 676 can be provided with a number of tabs 678 to facilitate attachment to the second carrier member 618 with, for example, rivets 679. The carrier cap 676 can be provided with a number of openings 680 arranged radially about a piloting shoulder 682. In one embodiment, the piloting shoulder 682 cooperates with a mating shoulder 684 formed on the spring carrier 668.
During operation of the IVT 600, torque can be limited to a predetermined value by using the torque limiter 630. The main shaft 610 is adapted to receive a rotational power from the pulley 606. The rotational power is transferred to the first carrier member 616 and the spring carrier 668. The spring carrier 668 transfers the rotational power to the second carrier member 618 via the springs 664. The springs 664 are sized appropriately so that the springs 664 deflect when an output torque is above a predetermined value or in the case when a torque on the second carrier member 618 is above a predetermined value. The deflection of springs 664 corresponds to a rotation of the second carrier member 618 with respect to the first carrier member 616 thereby shifting the transmission ratio. The shift in transmission ratio reduces the torque on the second carrier member 618.
Turning now to
Passing now to
Referring now to
Turning now to
During assembly of the IVT 600, for example, a fluid is added to the sump 952. In some embodiments, the volume of the sump 952 can be small, therefore variation in the fluid volume added to the sump 952 can have a significant influence on the fill depth 954. In some instances, the fill depth 954 can be high enough to cause fluid in the sump 952 to contact the rotating components 955. Contact between the fluid in the sump 952 and the rotating components 955 can create drag and windage, which are known to be problematic. However, in certain instances, it may be desirable to increase the volume of fluid added to the sump 952. For example, increasing the volume of fluid may improve thermal characteristics, durability, and maintenance. Therefore, the hydraulic system 952 can be implemented to facilitate the increase in fluid volume added to the sump 952 and maintain a fill depth 954 below the rotating components 955.
During operation of the IVT 600, for example fluid is drawn from the sump 952 by the pump 956, which lowers the fill depth 954. The fluid is pressurized and delivered by the pump 956 to the reservoir 958. The reservoir 958 receives pressurized fluid- and fills the volume of the reservoir 958. The first and second orifices 960, 962 are sized appropriately so that once the reservoir 958 is under pressure, fluid can flow from the first orifice 960 while substantially no fluid flows from the second orifice 962. In some embodiments, the second orifice 962 can be a check valve that is configured to be open when the reservoir 958 is depressurized, and closed when the reservoir 958 is pressurized. The fluid flow from the first orifice 960 is directed to the rotating components 955 to provide lubrication and cooling. During operation of the IVT 600, for example, the reservoir 958 accumulates a volume of fluid. Once operation of the IVT 600 ceases, the accumulated volume drains from the reservoir 958 and returns to the sump 952.
Referring now to
Referring specifically now to
It should be noted that the description above has provided dimensions for certain components or subassemblies. The mentioned dimensions, or ranges of dimensions, are provided in order to comply as best as possible with certain legal requirements, such as best mode. However, the scope of the inventions described herein are to be determined solely by the language of the claims, and consequently, none of the mentioned dimensions is to be considered limiting on the inventive embodiments, except in so far as any one claim makes a specified dimension, or range of thereof, a feature of the claim.
The foregoing description details certain embodiments of the invention. It will be appreciated, however, that no matter how detailed the foregoing appears in text, the invention can be practiced in many ways. As is also stated above, it should be noted that the use of particular terminology when describing certain features or aspects of the invention should not be taken to imply that the terminology is being re-defined herein to be restricted to including any specific characteristics of the features or aspects of the invention with which that terminology is associated.
Claims
1. An infinitely variable transmission (IVT) having a longitudinal axis, the IVT comprising:
- a main shaft arranged along the longitudinal axis, the main shaft provided with a plurality of helical splines;
- a plurality of traction planet assemblies arranged angularly about the longitudinal axis;
- a first carrier member coupled to each of the traction planet assemblies, the first carrier member provided with a plurality of radially off-set slots, the first carrier member configured to guide the traction planet assemblies;
- a second carrier member coupled to each of the traction planet assemblies, the second carrier member provided with a plurality of radial slots, wherein the first and second carrier members are coupled to a rotational power source; and
- a shifting mechanism comprising: a shift fork having a pivot pin off-set from the longitudinal axis; a carrier driver nut operably coupled to the shift fork, the carrier driver nut having an inner bore configured to engage the helical splines of the main shaft, the carrier driver nut configured to rotate about the longitudinal axis, wherein a movement of the shift fork about the pivot pin corresponds to an axial movement of the carrier driver nut, and wherein an axial movement of the carrier driver nut corresponds to a rotation of the first carrier member with respect to the second carrier member.
2. The IVT of claim 1, further comprising a first traction ring in contact with each traction planet assembly, the first traction ring substantially non-rotatable about the main shaft.
3. The IVT of claim 2, further comprising a second traction ring in contact with each traction planet assembly, the second traction ring adapted to provide a power output from the IVT.
4. The IVT of claim 3, further comprising an output shaft operably coupled to the second traction ring.
5. The IVT of claim 4, further comprising a disengagement mechanism operably coupled to the output shaft.
6. The IVT of claim 5, further comprising a torque limiter coupled to the second carrier member.
7. The IVT of claim 6, wherein the torque limiter is coupled to the main shaft.
8. The IVT of claim 7, wherein the torque limiter comprises a plurality of springs operably coupled to the second carrier member and the main shaft.
9. A shifting mechanism for an infinitely variable transmission (IVT) having a main shaft arranged along a longitudinal axis of the IVT, a plurality of traction planet assemblies arranged angularly about the main shaft, the traction planet assemblies coupled to first and second carrier members, wherein the first carrier member is provided with a plurality of radially off-set guide slots, the first and second carrier members adapted to receive a rotational power, the shifting mechanism comprising:
- a shift fork having a pivot axis off-set from the longitudinal axis; and
- a carrier driver nut operably coupled to the shift fork, the carrier driver nut having a inner bore configured to engage a plurality of helical splines formed on the main shaft, the carrier driver nut configured to rotate about the longitudinal axis, the carrier driver nut adapted to axially translate along the longitudinal axis, wherein a movement of the shift fork about the pivot pin corresponds to an axial movement of the carrier driver nut, and wherein an axial movement of the carrier driver nut corresponds to a rotation of the first carrier member with respect to the second carrier member.
10. The shifting mechanism of claim 9, further comprising a shift collar operably coupled to the shift fork.
11. The shifting mechanism of claim 10, further comprising a bearing coupled to the shift collar, the bearing adapted to couple to the carrier driver nut.
12. The shifting mechanism of claim 9, further comprising a rocker arm operably coupled to the shift fork.
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Type: Grant
Filed: Aug 19, 2013
Date of Patent: May 13, 2014
Patent Publication Number: 20130331218
Assignee: Fallbrook Intellectual Property Company LLC (Cedar Park, TX)
Inventors: Charles B. Lohr (Austin, TX), John W. Sherrill (Round Rock, TX), Brad P. Pohl (Leander, TX), Robert Dawson (Cedar Park, TX), Corey Pew (Austin, TX)
Primary Examiner: Roger Pang
Application Number: 13/970,035
International Classification: F16H 15/40 (20060101);
